Energy-saving tower type heat exchange device and control method thereof

Abstract

The invention discloses an energy-saving tower type heat exchange device and a control method thereof, and the energy-saving tower type heat exchange device comprises a heat exchange part which comprises a first heat exchanger and a second heat exchanger; the refrigerant supply component is selectively communicated and connected with the first heat exchanger and the second heat exchanger through a fluid pipeline; the controller comprises a first temperature sensor, a second temperature sensor and a wind speed sensor, the first temperature sensor is arranged on the outer side wall of the first heat exchanger, and the second temperature sensor is arranged on the outer side wall of the second heat exchanger; when the temperature value of the area corresponding to any heat exchanger is lower than a preset first temperature threshold value, the controller controls the refrigerant supply component to cut off refrigerant supply to the heat exchanger, and when the temperature value of the area corresponding to any heat exchanger is higher than a preset second temperature threshold value, the controller controls the refrigerant supply component to recover refrigerant supply to the heat exchanger. Heat exchange efficiency can be improved, and energy consumption is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of heat exchange equipment, and in particular to an energy-saving tower heat exchange device and a control method thereof. Background Art

[0002] Existing heat exchangers generally suffer from low heat exchange efficiency and high energy consumption. Traditional heat exchangers typically utilize a fixed heat exchange structure, which cannot dynamically adjust the heat exchange intensity based on actual operating conditions, resulting in significant energy waste. In tower-type heat exchangers in particular, due to uneven ambient temperature distribution, a fixed refrigerant flow rate can result in overcooling in some areas and insufficient heat exchange in others. Furthermore, existing systems lack intelligent temperature monitoring and refrigerant supply control systems, making precise energy-saving operation difficult. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides an energy-saving tower heat exchange device that can improve heat exchange efficiency and reduce energy consumption.

[0004] The present invention also provides a control method for the energy-saving tower heat exchange device.

[0005] An energy-saving tower heat exchange device according to a first embodiment of the present invention includes:

[0006] A heat exchange component comprising a first heat exchanger and a second heat exchanger;

[0007] a refrigerant supply component, selectively connected to the first heat exchanger and the second heat exchanger via a fluid pipeline;

[0008] a controller comprising a first temperature sensor, a second temperature sensor, and a wind speed sensor, wherein the first temperature sensor is disposed on an outer side wall of the first heat exchanger, and the second temperature sensor is disposed on an outer side wall of the second heat exchanger;

[0009] In which, the controller obtains the detection temperature of the first temperature sensor and the second temperature sensor in real time. When the temperature value of the corresponding area of any heat exchanger is lower than the preset first temperature threshold, the controller controls the refrigerant supply component to cut off the refrigerant supply to the heat exchanger. When the temperature of the area corresponding to any heat exchanger is higher than the preset second temperature threshold, the controller controls the refrigerant supply component to resume the refrigerant supply to the heat exchanger.

[0010] An energy-saving tower heat exchange device according to an embodiment of the present invention has at least the following beneficial effects: by setting a first heat exchanger and a second heat exchanger, and combining the intelligent control mechanism of the refrigerant supply component and the controller, efficient and energy-saving control of the heat exchange process is achieved. Specifically, the controller monitors the temperature changes of the outer walls of the two heat exchangers in real time through the first and second temperature sensors, and automatically controls the start and stop of the refrigerant supply components based on the set first and second temperature thresholds, thereby avoiding continuous cooling when not necessary and effectively reducing energy consumption; when the temperature of a heat exchange area is lower than the set low-temperature threshold, the system automatically cuts off the refrigerant supply to that area to prevent energy waste caused by excessive cooling; when the temperature rises above the high-temperature threshold, the system resumes cooling, ensuring heat exchange efficiency while achieving on-demand energy supply and improving the operating efficiency of the entire system; the refrigerant supply components only operate under necessary conditions, reducing unnecessary start-up times and operating time, reducing equipment wear, helping to extend the service life of the heat exchange device and related components, and reducing maintenance frequency and cost; the configuration of a wind speed sensor can further optimize the impact of environmental factors on heat exchange efficiency, improve the control system's adaptability to changes in external conditions, and make the entire heat exchange device have a higher level of intelligence and automation; the tower structure has a compact design and high space utilization, and is suitable for a variety of industrial cooling scenarios, especially for applications requiring zoned temperature control and energy saving and consumption reduction, and has good promotion value and application prospects.

[0011] According to some embodiments of the present invention, when applied to a cold storage, the first heat exchanger is arranged in the area above the cold storage door, the second heat exchanger is arranged in the central area of the top of the cold storage, the first temperature sensor is used to detect the temperature at the position of the cold storage door, the second temperature sensor is used to detect the temperature of the central area inside the cold storage, and the wind speed sensor is arranged in the air flow channel between the central area of the cold storage and the door;

[0012] Wherein, (1) when the first temperature sensor detects that the temperature of the area above the cold storage door is higher than the second temperature threshold, the refrigerant supply of the first heat exchanger is turned on;

[0013] (2) If the second temperature sensor detects that the temperature of the top central area of the cold storage is lower than the first temperature threshold, but the wind speed sensor detects that the current wind direction is from the second heat exchanger to the first heat exchanger, and the wind speed value exceeds 3m / s, the refrigerant supply to the second heat exchanger is forcibly maintained;

[0014] (3) When any of the following conditions is met, the refrigerant supply to the second heat exchanger is shut off:

[0015] The wind speed value drops below 2m / s;

[0016] The temperature of the area corresponding to the first heat exchanger drops below a first temperature threshold;

[0017] The cold storage door remains closed for more than 30 seconds. By introducing a wind speed sensor and comprehensively considering airflow direction and speed, the system can more accurately predict cooling capacity distribution trends. Compared with traditional control systems that rely solely on temperature feedback, this device significantly improves its adaptability to disturbances such as frequent door openings and the movement of goods in and out, enhancing the system's stability and intelligence.

[0018] According to some embodiments of the present invention, when applied to outdoor power facilities, the first heat exchanger is arranged on the direct sunlight side of the power equipment, the second heat exchanger is arranged on the shady side of the power equipment, and the wind speed sensor is arranged on the top of the power equipment to detect the real-time wind speed;

[0019] Wherein: (1) when the first temperature sensor detects that the temperature on the side directly exposed to the sun is higher than a second temperature threshold, the refrigerant supply to the first heat exchanger is turned on;

[0020] (2) If the wind speed sensor detects that the real-time wind speed exceeds 4 m / s, and the second temperature sensor detects that the temperature of the corresponding area of the second heat exchanger rises by more than 5°C within 10 minutes, the refrigerant supply of the second heat exchanger is forcibly started;

[0021] (3) When the real-time wind speed drops below 2 m / s and the temperature of the area corresponding to the second heat exchanger is lower than the first temperature threshold, the refrigerant supply to the second heat exchanger is turned off. If the wind speed sensor detects that the current wind speed exceeds 4 m / s, and the second temperature sensor detects that the temperature on the shady side rises by more than 5°C in a short period of time, indicating that the external wind flow may carry heat from the direct surface to the shady side, the system will forcibly start the refrigerant supply to the second heat exchanger, effectively dealing with the problem of heat diffusion caused by wind power and ensuring the balance and stability of the overall temperature field of the equipment.

[0022] According to some embodiments of the present invention, the controller further comprises a pressure sensor, which is disposed in a liquid outlet pipe of the refrigerant supply component and is electrically connected to the controller;

[0023] When the second heat exchanger maintains forced cooling due to wind speed, if the refrigerant supply pressure to the first heat exchanger is insufficient, the refrigerant supply component prioritizes supply to the first heat exchanger. Dynamically adjusting refrigerant allocation priorities avoids wasting refrigerant resources in non-critical areas, achieving more scientific and rational energy utilization and improving overall system efficiency.

[0024] According to some embodiments of the present invention, the refrigerant supply component further includes a filter cartridge disposed within the liquid outlet pipe of the refrigerant supply component. Both ends of the filter cartridge are connected to the liquid outlet pipe via flanges, and a V-shaped filter screen is disposed within the filter cartridge. The V-shaped filter screen can more effectively collect and secure impurities, reducing the risk of them entering the heat exchanger or other critical components. The flange connection allows for easy assembly and disassembly of the filter cartridge without the need for special tools or complex operations, facilitating regular inspection and cleaning of the V-shaped filter screen to ensure its continued efficient filtering performance.

[0025] According to some embodiments of the present invention, a heat exchange device includes a first heat exchange fin and a second heat exchange fin stacked together. The first heat exchange fin is provided with a first slot extending through it, and the second heat exchange fin is provided with a second slot extending through it. The projections of the first slot and the second slot along the depth direction partially overlap or are completely offset. This allows the entire heat dissipation area of both heat exchange fins to participate in the evaporative heat transfer process, thereby improving heat exchange efficiency.

[0026] According to some embodiments of the present invention, the first heat exchanger is provided with a first heat exchange fin, which is arranged on one side along the length of the first slot; the second heat exchanger is provided with a second heat exchange fin, which is arranged on one side along the length of the second slot; the first heat exchange fin is arranged at an angle away from the first heat exchange fin, and the second heat exchange fin is arranged at an angle away from the second heat exchange fin. The inclined arrangement of the fins achieves a higher heat exchange area density within a limited space, making the heat exchanger structure more compact, facilitating a reduction in overall unit size, and suitable for space-constrained applications.

[0027] According to some embodiments of the present invention, the heat exchange component further includes a water distribution pipe row, which is sandwiched above the first heat exchange fin and the second heat exchange fin. The water distribution pipe row includes a first accommodating chamber and a second accommodating chamber, the first accommodating chamber and the second accommodating chamber extending along the length of the water distribution pipe row, one end of the water distribution pipe row is connected to a water supply pipe, a water guide hole is provided between the first accommodating chamber and the second accommodating chamber, the water guide hole is provided at the bottom of the first accommodating chamber, and the inner side wall of the second accommodating chamber abuts the first heat exchange fin and the second heat exchange fin, respectively. This design helps ensure that the cooling water can be quickly and evenly dispersed when it contacts the heat exchange pipe row, forming a continuous water film covering the entire heat exchange surface, thereby improving heat exchange efficiency.

[0028] According to some embodiments of the present invention, the volume of the first accommodating chamber is V1, and the volume of the second accommodating chamber is V2, satisfying V1:V2 ≥ 3. The larger first accommodating chamber can effectively store and buffer the incoming cooling water, ensuring a smooth and continuous water supply process, avoiding uneven water distribution caused by water flow fluctuations, and achieving precise distribution and uniform outflow of cooling water. Since the volume of the second accommodating chamber is smaller, the water flow rate within it is relatively fast, which helps the cooling water pass through the water distribution channel more efficiently and be guided by the guide vanes to the surface of the heat exchange tube array, forming a more uniform water film distribution.

[0029] According to a second aspect of the present invention, the control method includes the energy-saving tower heat exchange device of the first aspect, wherein the control method includes:

[0030] S1. Real-time monitoring of the temperature and environmental parameters of the corresponding areas of each heat exchanger;

[0031] S2. When the temperature of any heat exchanger corresponding area exceeds the preset second temperature threshold, the refrigerant supply component is controlled to open the refrigerant supply of the heat exchanger;

[0032] S3. If the heat exchange device is used in a cold storage, execute the cold storage-specific control logic:

[0033] (a) when the temperature of the first heat exchanger (door zone) is higher than the second temperature threshold, starting the refrigerant supply thereof;

[0034] (b) when it is detected that the wind speed directed from the second heat exchanger (central area) to the first heat exchanger exceeds 3 m / s and the central area temperature is lower than the first temperature threshold, forcibly maintaining the refrigerant supply to the second heat exchanger;

[0035] (c) monitoring the refrigerant pressure in real time and, if the pressure is lower than a dynamic threshold, preferentially cutting off the refrigerant supply to the second heat exchanger;

[0036] If the heat exchange device is used in an outdoor power facility, execute the power facility-specific control logic:

[0037] (a) when the temperature of the first heat exchanger (sun-direct-side) exceeds a second temperature threshold, starting the refrigerant supply;

[0038] (b) When the wind speed exceeds 4 m / s and the temperature of the second heat exchanger (on the shady side) rises by more than 5°C within 10 minutes, the refrigerant supply to the second heat exchanger is forcibly started;

[0039] (c) If the refrigerant pressure is insufficient, the second heat exchanger will be started and stopped intermittently according to the preset cycle (≤30 seconds);

[0040] S5. When any of the following conditions is met, the refrigerant supply to the corresponding heat exchanger is shut off:

[0041] (a) The temperature drops below the first temperature threshold;

[0042] (b) The wind speed is lower than the scenario setting threshold (cold storage: 2 m / s; power facilities: 2 m / s);

[0043] (c) The cold storage door is closed for more than 30 seconds;

[0044] S6. When the pressure difference between the two ends of the filter cartridge exceeds 200Pa or the refrigerant pressure remains below 200Pa for more than 5 seconds, a maintenance alarm signal is generated and sent to the user terminal.

[0045] The control method according to an embodiment of the present invention has at least the following beneficial effects: by real-time monitoring of the temperature and environmental parameters (such as wind speed and refrigerant pressure) in the corresponding areas of each heat exchanger, and dynamically controlling the start and stop of the refrigerant supply components based on preset temperature thresholds, it achieves on-demand cooling, avoids unnecessary energy waste, and effectively improves the overall energy efficiency of the system. The control method also provides separate control logic for cold storage and outdoor power facilities. For example, in cold storage, the control method considers local temperature rise and airflow disturbances caused by frequent door opening and closing; in outdoor power facilities, the control method focuses on addressing direct sunlight and wind-induced heat transfer effects. This differentiated control strategy significantly improves the device's adaptability and operational reliability under various complex operating conditions. When the pressure differential across the filter cartridge exceeds 200 Pa or the duration of abnormal refrigerant pressure exceeds a set threshold (such as 5 seconds), the controller generates a maintenance alarm signal and sends it to the user terminal, reminding the operator to clean the filter or check the refrigerant system status in a timely manner. This function helps to detect potential fault risks in advance, reduce sudden downtime, and improve system operation safety and maintenance efficiency.

[0046] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0047] The present invention will be further described below with reference to the accompanying drawings and embodiments, in which:

[0048] Figure 1 This is a schematic diagram of the connection between the heat exchange component and the filter cartridge according to an embodiment of the present invention;

[0049] Figure 2 This is a schematic diagram of the assembly of a heat exchange component and a water distribution pipe bank according to an embodiment of the present invention;

[0050] Figure 3 This is a schematic diagram of the operation of the refrigerant delivery assembly according to an embodiment of the present invention;

[0051] Figure 4 is a schematic diagram of a first heat sink and a second heat sink according to an embodiment of the present invention;

[0052] Figure 5 A schematic diagram of a water distribution pipe bank according to an embodiment of the present invention;

[0053] Figure 6 for Figure 5 Enlarged schematic diagram of point A in the middle.

[0054] Figure numerals: heat exchanger 100; liquid outlet pipe 120; filter cartridge 130; water distribution pipe row 140; refrigerant supply component 150; first heat exchanger 160; second heat exchanger 170; first heat exchange plate 180; second heat exchange plate 190; first heat exchange fin 200; second heat exchange fin 210; first accommodating chamber 220; second accommodating chamber 230; water guide hole 240; guide plate 250; first slot 260; second slot 270; secondary water supply hole 280. DETAILED DESCRIPTION

[0055] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0056] In the description of the present invention, it should be understood that descriptions involving orientations, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, they cannot be understood as limitations on the present invention.

[0057] In the description of the present invention, "several" means one or more, "many" means more than two, "greater than," "less than," and "exceed" are understood to exclude the number itself, while "above," "below," and "within" are understood to include the number itself. The use of "first" and "second" in the description is solely for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, implicitly specifying the number of the indicated technical features, or implicitly specifying the order of the indicated technical features.

[0058] In the description of the present invention, unless otherwise explicitly defined, terms such as "set," "install," and "connect" should be interpreted broadly. Those skilled in the art can reasonably determine the specific meanings of these terms in the present invention based on the specific content of the technical solution. In the description of the present invention, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with such embodiment or example are included in at least one embodiment or example of the present invention. In this specification, schematic representations of these terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. In the description of this specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with such embodiment or example are included in at least one embodiment or example of the present invention. In this specification, schematic representations of these terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0059] In existing technologies, tower heat exchangers generally suffer from low heat exchange efficiency and high energy consumption. Traditional equipment utilizes a fixed heat exchange structure, making it impossible to dynamically adjust the heat exchange intensity based on actual operating conditions, resulting in significant energy waste. In scenarios with uneven ambient temperature distribution, a fixed refrigerant supply method can lead to both regional overcooling and insufficient heat exchange. For example, in cold storage applications, the temperature difference between the door area and the central interior area is significant, making it difficult for existing equipment to achieve precise temperature control.

[0060] Therefore, this application proposes an energy-saving tower heat exchanger, comprising a heat exchange component, a refrigerant supply component 150, and a controller. The heat exchange component comprises a first heat exchanger 160 and a second heat exchanger 170, with the refrigerant supply component 150 selectively connected to both via a fluid conduit. The controller is equipped with a first temperature sensor and a second temperature sensor located on the outer wall of the heat exchanger 100 to detect temperatures in real time and control the flow of refrigerant.

[0061] Among them, the heat exchange component refers to a partitioned temperature control structure with independent heat exchange function, which can be implemented by a plate heat exchanger 100 or a tube-fin heat exchanger 100. Its partition setting can implement differential adjustments for different temperature zones. The refrigerant supply component 150 refers to a circulation system with a flow control valve, which specifically adopts an electromagnetic three-way valve to realize the switching of the refrigerant path, and ensures the distribution of refrigerant on demand through selective conduction. The controller refers to a control unit with data processing capabilities, which can be implemented by a PLC or an embedded controller, and collects the temperature data of the heat exchange area in real time through a temperature sensor. The first temperature threshold refers to the minimum temperature critical value for maintaining normal operation of the equipment, and the second temperature threshold refers to the temperature critical value for starting cooling. The specific value can be set according to the application scenario.

[0062] Specifically, when the temperature of the area corresponding to a certain heat exchanger 100 is lower than the first temperature threshold, the controller immediately cuts off the refrigerant supply in the area to prevent energy waste caused by overcooling. When the temperature rises to the second temperature threshold, the controller restarts the refrigerant supply to ensure timely response to heat exchange needs. This dynamic control mechanism accurately senses the actual temperature changes in the heat exchange area through an external temperature sensor, and combines it with dual-threshold judgment logic to achieve precise start and stop control of the refrigerant supply. In the cold storage application scenario, independent heat exchangers 100 are respectively configured in the door area and the top central area. When the door is frequently opened, causing the local temperature to rise, the system only starts the refrigerant supply in the corresponding area to avoid unnecessary cooling of the entire storage area.

[0063] Compared to existing technologies, traditional devices use a monolithic heat exchange structure and a fixed refrigerant flow rate, making them unable to cope with local temperature fluctuations. This solution achieves dynamic refrigerant flow distribution by zoning the heat exchanger 100 and coordinating it with an intelligent control system. This solution also places temperature sensors on the outer wall of the heat exchanger 100, improving the accuracy of temperature monitoring.

[0064] Through the above technical solution, this application effectively solves the energy waste problem caused by uneven regional temperatures and achieves precise control of refrigerant supply. The zoned temperature control structure avoids energy loss caused by overall cooling, and the dual-threshold control strategy reduces the number of equipment starts and stops while ensuring effective heat exchange. The external temperature sensor improves the operating efficiency of the heat exchange system.

[0065] The present application further proposes an implementation method of an energy-saving tower heat exchange device in a cold storage scenario. In this implementation method, the first heat exchanger 160 is arranged in the area above the cold storage door, and the second heat exchanger 170 is arranged in the central area at the top of the cold storage. The first temperature sensor is used to monitor the temperature of the door position, the second temperature sensor is used to monitor the temperature of the central area in the warehouse, and the wind speed sensor is arranged in the air flow channel between the central area and the door body. When the temperature of the area above the door body exceeds the preset threshold, the refrigerant supply of the first heat exchanger 160 is turned on. If the temperature in the central area of the warehouse has reached the standard at this time, but the wind speed is detected to be higher than 3m / s and the airflow direction is directed to the door body, the refrigerant supply of the second heat exchanger 170 is forced to be maintained. When the wind speed drops below 2m / s, the door area temperature reaches the standard, or the door body is closed for more than 30 seconds, the refrigerant supply of the second heat exchanger 170 is turned off.

[0066] Specifically, when the cold storage door is frequently opened, external hot air first invades the area above the door. The first heat exchanger 160 arranged in this area triggers the supply of refrigerant through a temperature sensor, forming a local cooling barrier. At the same time, the second heat exchanger 170 in the central area of the storage should stop supplying cold air after the temperature reaches the standard. However, when the wind speed sensor detects high-speed airflow flowing from the central area to the door, it is judged that there is a risk of cold air escape, and the second heat exchanger 170 is forced to maintain operation to form a reverse cold air curtain. When the door is closed for more than 30 seconds, the system automatically terminates the forced operation of the second heat exchanger 170 to avoid overcooling caused by the cessation of airflow.

[0067] Compared to existing technologies, traditional cold storage heat exchange systems control refrigerant supply based solely on the temperature of a single zone, making them unable to cope with dynamic airflow changes when the door is opened. This solution establishes a multi-dimensional monitoring system using three sets of sensors. This system incorporates compensatory control of airflow direction and speed in addition to temperature control, thus overcoming the limitations of static temperature thresholds.

[0068] Through the above-mentioned technical solution, this application effectively solves the technical problem of unbalanced heat and cold distribution between the cold storage door area and the central area. Through the targeted deployment of heat exchangers 100 and sensor networks, coordinated control of refrigerant supply and airflow disturbances is achieved, ensuring stable temperature in the core area of the storage while reducing cooling losses caused by drafts. The combined use of a forced maintenance mechanism and multiple shutdown conditions enables the system to both cope with sudden heat load shocks and avoid unnecessary energy consumption in low-temperature areas.

[0069] This application further proposes an energy-saving tower heat exchanger for outdoor power facilities, comprising a first heat exchanger 160 disposed on the sun-facing side of the power equipment, a second heat exchanger 170 disposed on the shaded side, and a wind speed sensor disposed on the top of the equipment. When the first temperature sensor detects that the sun-facing side temperature is above a set threshold, the refrigerant supply to the first heat exchanger 160 is activated. When the wind speed exceeds the threshold and the shaded side temperature rises above a safety threshold within a set time, the refrigerant supply to the second heat exchanger 170 is forcibly activated. When the wind speed falls below the threshold and the shaded side temperature meets the safety threshold, the refrigerant supply to the second heat exchanger 170 is shut off.

[0070] Specifically, when the temperature on the side directly exposed to the sun exceeds a preset upper limit, the first heat exchanger 160 automatically starts to offset the solar radiation heat load. When the wind speed exceeds the safety threshold and the temperature on the shady side rises sharply in a short period of time, the system identifies it as harmful wind interference resulting in a decrease in heat dissipation efficiency. At this time, the second heat exchanger 170 is forced to start to supplement the heat dissipation capacity. When the wind speed decreases to a safe range and the temperature on the shady side stabilizes, the system automatically stops the operation of the second heat exchanger 170 to save refrigerant consumption. This solution can effectively distinguish between natural cooling wind and destructive turbulence by jointly analyzing the temperature change rate and wind speed vector data, and only starts the auxiliary heat exchanger 100 when it is really needed, avoiding misoperation caused by a single wind speed trigger in traditional solutions.

[0071] Compared with the existing technology, traditional heat dissipation devices for power equipment usually only control the supply of refrigerant based on the local temperature threshold, and are unable to identify the impact of wind speed direction on heat dissipation efficiency. For example, in the existing technology, when a high wind speed is detected, it may be misjudged as a beneficial heat dissipation condition and stop cooling, but the actual strong side wind will disrupt the normal convection path. This solution introduces a dual judgment mechanism of wind speed vector detection and temperature change rate, which can accurately identify harmful wind fields that cause a decrease in heat exchange efficiency and start compensatory cooling in time. Through the above technical solution, the present application solves the problem of local overheating of outdoor power facilities caused by complex wind field interference, and effectively prevents the temperature rise in the shaded area caused by harmful wind speeds.

[0072] The present application further proposes to set a pressure sensor in the liquid outlet pipe 120 of the refrigerant supply component 150, and the pressure sensor is electrically connected to the controller; when the second heat exchanger 170 is forced to maintain cooling due to wind speed conditions, if the refrigerant supply pressure of the first heat exchanger 160 is insufficient, the refrigerant supply component 150 will prioritize allocating refrigerant resources to the first heat exchanger 160.

[0073] Specifically, in forced cooling mode, the continuous operation of the second heat exchanger 170 may cause the refrigerant delivery pressure to disperse. The pressure sensor collects the fluid pressure value in the liquid outlet pipe 120 in real time and transmits the data to the controller for dynamic analysis. When insufficient pressure occurs in the core area where the first heat exchanger 160 is located, the controller immediately triggers the priority judgment program and concentrates the refrigerant to the first heat exchanger 160 by closing the solenoid valve of the second heat exchanger 170 or adjusting the flow direction of the three-way valve. This process is implemented through pressure threshold comparison and logical operations to ensure that the heat exchange needs of key areas are met first when the total system pressure is limited.

[0074] Compared to existing technologies, traditional solutions lack a dynamic monitoring mechanism for refrigerant delivery pressure, making it impossible to identify pressure distribution imbalances when multiple heat exchangers 100 operate in parallel. Existing equipment typically uses fixed flow distribution or simple sequential control, which prevents flexible allocation of refrigerant resources based on actual operating conditions. This solution achieves real-time optimization of refrigerant delivery pressure by establishing a closed-loop pressure feedback control system.

[0075] Through the above technical solution, this application effectively solves the problem of unbalanced refrigerant pressure distribution in forced cooling mode, avoiding the phenomenon of insufficient system pressure caused by simultaneous cooling in multiple zones. The heat exchanger 100 in the core area is guaranteed to have a stable refrigerant supply, preventing temperature runaway in key areas due to cooling interruptions, and overall improving the operational reliability of the heat exchange device under complex operating conditions.

[0076] The present application further proposes that the refrigerant supply component 150 also includes a filter cartridge 130, which is arranged in the liquid outlet pipe 120 of the refrigerant supply component 150. The two ends of the filter cartridge 130 are respectively connected to the liquid outlet pipe 120 through flanges, and a V-shaped filter screen is arranged in the filter cartridge 130.

[0077] A flange connection uses a flange with bolt holes as a pipe connector. Specifically, a carbon steel flange and rubber gasket are used for sealing. This connection method ensures the pipe's pressure-bearing capacity while facilitating assembly and disassembly for maintenance. A V-shaped filter is a structure composed of multiple sets of wire mesh folded together to form an angle. Specifically, it can be constructed using corrugated stainless steel mesh with a 60-degree angle. This asymmetric layout deflects the fluid path, increasing the filtration area while directing impurities to the angles of the mesh.

[0078] Specifically, when the refrigerant flows from the liquid outlet pipe 120 through the filter cartridge 130, the angled structure of the V-shaped filter mesh forces the fluid to change direction, and the solid particles collide with the surface of the mesh under the action of inertia and are captured. The V-shaped groove formed by the angle of the mesh can prevent impurities from directly accumulating in the vertical direction, maintaining the effective filtration area. When cleaning is required, the filter cartridge 130 can be removed as a whole for flushing or replacement by loosening the flange bolts. During the refrigerant circulation process, the corrugated structure of the V-shaped mesh can generate local turbulence, flushing the particles attached to the mesh and extending the service life of the filter element.

[0079] Compared to existing technologies, traditional tower heat exchangers often use flat disc filters. These flat structures are easily covered by impurities, resulting in a sudden increase in pressure drop and requiring shutdown and disassembly of the entire pipeline for maintenance. This solution uses V-shaped angled mesh to achieve a three-dimensional expansion of the filtration space, increasing the effective filtration area by approximately 40% while maintaining the same volume. Furthermore, the flange connection structure reduces maintenance time to one-third of traditional methods.

[0080] Through the above-mentioned technical solution, the present application effectively intercepts solid impurities such as metal debris and scale in the refrigerant, avoiding the decrease in heat transfer efficiency caused by blockage of the flow channel of the heat exchanger 100 and preventing impurities from abrading precision components such as pumps and valves. The modular flange connection design greatly shortens the maintenance cycle of the filter device and significantly improves the operational stability of the system. The self-cleaning properties of the V-shaped mesh can reduce the frequency of filter element replacement by approximately 50%, maintaining stable filtration performance under high-temperature and high-pressure conditions.

[0081] Reference Figure 4 and Figure 6 The present application further proposes a first heat exchange plate 180 and a second heat exchange plate 190 arranged in a stacked manner, wherein the first heat exchange plate 180 is penetrated by a first slot 260, and the second heat exchange plate 190 is penetrated by a second slot 270, and the projections of the first slot 260 and the second slot 270 along the depth direction partially overlap or are completely staggered.

[0082] Among them, the stacking arrangement refers to assembling two heat exchanger plates in a parallel stacking manner, which can be achieved by stamping aluminum alloy plates and then fixing them with bolts to form a plate structure stacked up and down. The first slot 260 refers to a through hole opened on the surface of the first heat exchanger plate 180, which can be achieved by rectangular or corrugated grooves. The second slot 270 is arranged on the second heat exchanger plate 190 in the same manner as the first slot 260, and its position is spatially dislocated with the first slot 260. Partial overlap of the projections means that the two slots have an overlapping area on the vertical projection plane, and complete dislocation means that there is no overlapping area on the projection plane.

[0083] Specifically, when the first heat exchange fin 180 and the second heat exchange fin 190 are stacked and assembled, with their projected portions overlapping, cooling water can simultaneously flow through the overlapping area of the two slots, exposing the heat dissipation area on the back of the first heat exchange fin 180 to the second slot 270, and the heat dissipation area on the back of the second heat exchange fin 190 to the first slot 260. When the slots are completely staggered, cooling water needs to flow through the backs of both heat exchange fins separately. This staggered arrangement of double-sided slots increases the heat transfer area of the heat exchange fins, allowing even the hidden heat dissipation area where the two fins overlap to participate in the heat exchange process.

[0084] Compared to existing technologies, traditional tower heat exchangers use symmetrical slotted structures, resulting in a fixed cooling water flow path and limited contact area, which can easily lead to uneven heat exchange. However, this solution utilizes a stacked slotted structure to increase the contact area between the cooling water and the heat exchanger fins while maintaining the same volume. By staggering the slots, the heat dissipation area on the back of the fins is fully utilized, significantly improving heat dissipation efficiency.

[0085] Through the above technical solution, the present application achieves uniform distribution of fluid on the surface and back of the heat exchange plate, reduces local overheating or overcooling, and improves heat exchange efficiency.

[0086] The present application further proposes that the first heat exchange fin 180 is provided with a first heat exchange fin 200, and the first heat exchange fin 200 is arranged on one side of the length direction of the first slot 260; the second heat exchange fin 190 is provided with a second heat exchange fin 210, and the second heat exchange fin 210 is arranged on one side of the length direction of the second slot 270; the first heat exchange fin 200 is inclined in a direction away from the first heat exchange fin 180, and the second heat exchange fin 210 is inclined in a direction away from the second heat exchange fin 190.

[0087] The first heat exchange fin 200 is a plate-like structure attached to the surface of the first heat exchange fin 180 and extending unilaterally along the length of the slot. Specifically, it can be integrally formed with the heat exchange fin using a stamping process. Its inclination angle away from the main body can be set to 20-45 degrees, accelerating heat transfer by increasing the contact area with the fluid. The second heat exchange fin 210 is similarly formed on the second heat exchange fin 190. Its inclination creates a spatially staggered arrangement with the first heat exchange fin 200, forming an asymmetric flow channel after stacking.

[0088] Specifically, when cooling water flows through the heat exchange fins, the first heat exchange fin 200 and the second heat exchange fin 210 form flow barriers on one side of their respective slots. This creates a cross-shaped flow channel, generating turbulence at the intersection of fluids at different levels. The tilt angle of the fins guides the fluid to form vertical component flows, significantly improving heat exchange efficiency.

[0089] The present application further proposes that the heat exchange component also includes a water distribution pipe row 140, which is clamped above the first heat exchange plate 180 and the second heat exchange plate 190. The water distribution pipe row 140 includes a first accommodating cavity 220 and a second accommodating cavity 230. The first accommodating cavity 220 and the second accommodating cavity 230 are extended along the length direction of the water distribution pipe row 140. One end of the water distribution pipe row 140 is connected to a water supply pipe. A water guide hole 240 is provided between the first accommodating cavity 220 and the second accommodating cavity 230. The water guide hole 240 is provided at the bottom of the first accommodating cavity 220, and the inner side walls of the second accommodating cavity 230 are respectively in contact with the first heat exchange plate 180 and the second heat exchange plate 190.

[0090] Among them, the water distribution pipe row 140 refers to the water supply structure arranged on the top of the heat exchange plate, which can be specifically implemented by an aluminum or copper tube body with a double cavity inside, and is used to guide the water flow to be distributed along the surface of the heat exchange plate. The first accommodating chamber 220 refers to the water storage chamber near the inlet of the water supply pipe, which can be specifically implemented by a tubular cavity structure with a cross-sectional area larger than that of the second accommodating chamber 230, and is used to temporarily store the input water flow and buffer pressure fluctuations. The second accommodating chamber 230 refers to the water distribution chamber in direct contact with the heat exchange plate, which can be specifically implemented by a flat tubular cavity structure extending along the length direction, and is used to evenly guide the water flow to the surface of the heat exchange plate. The water guide hole 240 refers to a water passage connecting the two cavities, which can be specifically implemented by a circular or elliptical through hole opened at the bottom of the first accommodating chamber 220, and the water flow is naturally caused to flow down to the second accommodating chamber 230 by gravity.

[0091] Specifically, after the water supply pipe injects water into the first accommodating chamber 220, the water is temporarily stored in the chamber. Because the volume of the first accommodating chamber 220 is significantly larger than that of the second accommodating chamber 230, the water forms a pressure buffer before entering the water guide hole 240, preventing water supply pressure fluctuations from directly affecting the water distribution process. The water guide hole 240 is located at the bottom of the first accommodating chamber 220. The water flows evenly into the second accommodating chamber 230 through gravity and diffuses along the length of the flat space of the second accommodating chamber 230. The inner wall of the second accommodating chamber 230 is in close contact with the heat exchange plate. The water directly wets the surface of the heat exchange plate through the contact surface, preventing the water from being lost in the non-contact area.

[0092] The traditional water distributor adopts a single-cavity straight-through structure, which leads to insufficient water pressure at the end. This solution realizes secondary water distribution by setting up a double-cavity structure. The first accommodating chamber 220 buffers the water flow pressure fluctuation, and the second accommodating chamber 230 uses gravity to maintain the end water distribution pressure, ensuring the uniformity of water distribution along the length of the heat exchanger.

[0093] It solves the problem of uneven water distribution caused by insufficient water pressure at the end of the water distribution pipe. The double-cavity structure forms pressure buffering and secondary water distribution, so that the water flow forms a stable coverage on the surface of the heat exchanger, thereby improving the evaporation heat exchange efficiency.

[0094] The present application further proposes a technical solution in which the volume ratio of the first accommodating cavity 220 to the second accommodating cavity 230 in the water distribution pipe row 140 is set to V1:V2≥3.

[0095] Specifically, after the water supply pipe injects water into the first chamber 220, its larger volume forms a water buffer. Under the action of gravity, the water flows through the bottom water guide hole 240 and enters the second chamber 230 at a constant flow rate. Because the second chamber 230 has a smaller volume and its sidewalls directly contact the heat exchange fins, the water builds up a stable pressure inside and then evenly penetrates the surface of the heat exchange fins through capillary action. When the ratio of V1 to V2 reaches 3:1, the amount of water stored in the first chamber 220 is sufficient to keep the heat exchange fins of the second chamber 230 continuously moist between water supply intervals, preventing localized drying caused by transient flow fluctuations.

[0096] Traditional water distribution pipes 140 use a single cavity or a dual-cavity structure with equal volumes. Water flows directly into the heat exchanger fins without being graded or buffered, which can easily cause overflow at the edges and insufficient wetting in the center. This solution utilizes a differentiated volume design to achieve two-stage water flow control. The first chamber 220 acts as a pressure buffer, while the second chamber 230 provides even distribution, eliminating the problem of liquid film rupture caused by water impact.

[0097] Reference Figure 5 In some embodiments, a plurality of guide vanes 250 are provided on the inner wall of the second accommodating chamber 230, and the plurality of guide vanes 250 are arranged at intervals along the length direction of the second accommodating chamber 230, and the tip of each guide vane 250 is arranged toward the water outlet end of the second accommodating chamber 230. This design can effectively divert and guide the water flow, break the surface tension of the water flow, thereby forming a more uniform and continuous water film on the surface of the heat exchange plate, and improving the evaporative cooling effect. In other embodiments, a secondary water replenishment hole 280 can also be provided in the middle of the water distribution pipe row 140 to ensure that sufficient water pressure is maintained in the first accommodating chamber 220. This design helps to ensure that the water flow stably flows from the first accommodating chamber 220 through the water guide hole 240 to the second accommodating chamber 230, thereby ensuring that a uniform and continuous water film can be formed on the surface of the heat exchange plate, thereby improving the overall heat exchange efficiency.

[0098] The present application further proposes a control method for an energy-saving tower heat exchanger, comprising the following steps: real-time monitoring of the temperature and environmental parameters of the corresponding areas of each heat exchanger 100; when the temperature of the corresponding area of any heat exchanger 100 exceeds a preset second temperature threshold, controlling the refrigerant supply component 150 to start the refrigerant supply of the heat exchanger 100; executing dedicated control logic according to the application scenario, combining the wind speed and temperature coupling relationship in the cold storage scenario to force the maintenance of heat exchange demand under high wind speed, and giving priority to ensuring the supply of key areas, and triggering emergency cooling through temperature mutation monitoring and wind speed interlocking in the power facility scenario, and adopting a priority supply method to alleviate the contradiction of insufficient pressure; when the temperature drops below the first temperature threshold, the wind speed is lower than the scene setting threshold, or the cold storage door is continuously closed for more than 30 seconds, the refrigerant supply of the corresponding heat exchanger 100 is turned off; and a maintenance alarm signal is generated and sent to the user terminal.

[0099] Specifically, this method achieves dynamic control through multi-sensor data fusion. In cold storage applications, when the temperature rises in the door area, triggering the refrigerant supply, if the central area is detected to be cold but with high-speed airflow, the cooling of this area is forced to be maintained to avoid temperature imbalance caused by airflow scouring. At the same time, the heat exchange needs of key parts of the door area are prioritized through refrigerant pressure monitoring. In outdoor power facility scenarios, emergency cooling is activated when the temperature of the direct sunlight side is abnormal. When a sudden temperature rise on the shady side is detected accompanied by strong winds, emergency compensatory cooling is used to meet the heat exchange needs.

[0100] Compared with existing technologies, traditional control methods rely solely on a single temperature parameter for on-off control, making them unable to cope with dynamic changes in complex environments. This method addresses the problem of misjudgment caused by airflow disturbances by establishing a linkage mechanism between wind speed and temperature. By setting up scenario-based control logic, precise control is implemented for special operating conditions such as frequent cold storage door openings and sudden temperature rises in electrical equipment. An intermittent start-stop strategy effectively mitigates the risk of equipment overload caused by insufficient refrigerant pressure, a condition lacking in existing technologies due to the lack of such adaptive pressure control methods.

[0101] Through the above technical solution, this application effectively solves the problem of excessive energy consumption caused by the fixed refrigerant supply of traditional heat exchange devices and realizes dynamic energy-saving control in different application scenarios. In cold storage scenarios, it avoids the loss of cooling capacity caused by frequent door openings. In power facility scenarios, it prevents equipment overheating caused by sudden temperature rise. At the same time, the pressure adaptive mechanism extends the service life of the equipment and reduces the probability of failure and downtime caused by system overload. The maintenance alarm function predicts system anomalies in advance, significantly reducing the risk of sudden equipment failure.

[0102] The embodiments of the present invention are described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Various changes can be made within the knowledge of ordinary technicians in the relevant technical field without departing from the scope of the present invention.

Claims

1. An energy-saving tower heat exchange device, characterized in that: include: A heat exchange component comprising a first heat exchanger and a second heat exchanger; a refrigerant supply component, selectively connected to the first heat exchanger and the second heat exchanger via a fluid pipeline; a controller comprising a first temperature sensor, a second temperature sensor, and a wind speed sensor, wherein the first temperature sensor is disposed on an outer side wall of the first heat exchanger, and the second temperature sensor is disposed on an outer side wall of the second heat exchanger; In which, the controller obtains the detection temperature of the first temperature sensor and the second temperature sensor in real time. When the temperature value of the corresponding area of any heat exchanger is lower than the preset first temperature threshold, the controller controls the refrigerant supply component to cut off the refrigerant supply to the heat exchanger. When the temperature of the area corresponding to any heat exchanger is higher than the preset second temperature threshold, the controller controls the refrigerant supply component to resume the refrigerant supply to the heat exchanger.

2. The energy-saving tower heat exchange device according to claim 1, characterized in that: When applied to a cold storage, the first heat exchanger is arranged in the area above the cold storage door, the second heat exchanger is arranged in the central area of the top of the cold storage, the first temperature sensor is used to detect the temperature at the position of the cold storage door, the second temperature sensor is used to detect the temperature of the central area inside the cold storage, and the wind speed sensor is arranged in the air flow channel between the central area of the cold storage and the door; Wherein, (1) when the first temperature sensor detects that the temperature of the area above the cold storage door is higher than the second temperature threshold, the refrigerant supply to the first heat exchanger is turned on; (2) If the second temperature sensor detects that the temperature of the top central area of the cold storage is lower than the first temperature threshold, but the wind speed sensor detects that the current wind direction is from the second heat exchanger to the first heat exchanger, and the wind speed value exceeds 3m / s, the refrigerant supply to the second heat exchanger is forcibly maintained; (3) When any of the following conditions is met, the refrigerant supply to the second heat exchanger is shut off: The wind speed value drops below 2m / s; The temperature of the area corresponding to the first heat exchanger drops below a first temperature threshold; The cold storage door remains closed for more than 30 seconds.

3. The energy-saving tower heat exchange device according to claim 1, characterized in that: When used in outdoor power facilities, the first heat exchanger is arranged on the direct sunlight side of the power equipment, the second heat exchanger is arranged on the shady side of the power equipment, and the wind speed sensor is arranged on the top of the power equipment to detect the real-time wind speed; Wherein: (1) when the first temperature sensor detects that the temperature on the side directly exposed to the sun is higher than a second temperature threshold, the refrigerant supply to the first heat exchanger is turned on; (2) If the wind speed sensor detects that the real-time wind speed exceeds 4 m / s, and the second temperature sensor detects that the temperature of the corresponding area of the second heat exchanger rises by more than 5°C within 10 minutes, the refrigerant supply to the second heat exchanger is forcibly started; (3) When the real-time wind speed drops below 2 m / s and the temperature of the area corresponding to the second heat exchanger is lower than the first temperature threshold, the refrigerant supply to the second heat exchanger is turned off.

4. An energy-saving tower heat exchange device according to claim 2 or 3, characterized in that: The controller further includes a pressure sensor, which is disposed in the liquid outlet pipe of the refrigerant supply component and is electrically connected to the controller; When the second heat exchanger maintains forced cooling due to the wind speed, if the refrigerant supply pressure of the first heat exchanger is insufficient, the refrigerant supply component gives priority to supplying the first heat exchanger.

5. The energy-saving tower heat exchange device according to claim 1, characterized in that: The refrigerant supply component also includes a filter cartridge, which is arranged in the liquid outlet pipe of the refrigerant supply component. Both ends of the filter cartridge are connected to the liquid outlet pipe through flanges respectively, and a V-shaped filter screen is arranged in the filter cartridge.

6. The energy-saving tower heat exchange device according to claim 1, characterized in that: The heat exchange device includes a first heat exchange plate and a second heat exchange plate arranged in a stacked manner. The first heat exchange plate is penetrated by a first slot, and the second heat exchange plate is penetrated by a second slot. The projections of the first slot and the second slot in the depth direction partially overlap or are completely staggered.

7. The energy-saving tower heat exchange device according to claim 6, characterized in that: The first heat exchange plate is provided with a first heat exchange fin, which is arranged on one side of the length direction of the first slot; the second heat exchange plate is provided with a second heat exchange fin, which is arranged on one side of the length direction of the second slot; the first heat exchange fin is inclined in a direction away from the first heat exchange plate, and the second heat exchange fin is inclined in a direction away from the second heat exchange plate.

8. The energy-saving tower heat exchange device according to claim 6, characterized in that: The heat exchange component also includes a water distribution pipe row, which is clamped above the first heat exchange plate and the second heat exchange plate. The water distribution pipe row includes a first accommodating chamber and a second accommodating chamber. The first accommodating chamber and the second accommodating chamber extend along the length direction of the water distribution pipe row. One end of the water distribution pipe row is connected to a water supply pipe. A water guide hole is provided between the first accommodating chamber and the second accommodating chamber. The water guide hole is provided at the bottom of the first accommodating chamber, and the inner side walls of the second accommodating chamber are respectively in contact with the first heat exchange plate and the second heat exchange plate.

9. The energy-saving tower heat exchange device according to claim 8, characterized in that: The volume of the first accommodating chamber is V1, and the volume of the second accommodating chamber is V2, satisfying V1:V2≥3.

10. A control method for an energy-saving tower heat exchanger, characterized in that: Applied to the energy-saving tower heat exchange device according to any one of claims 1 to 9, the control method comprises: S1. Real-time monitoring of the temperature and environmental parameters of each heat exchanger area; S2. When the temperature of any heat exchanger corresponding area exceeds a preset second temperature threshold, the refrigerant supply component controls the refrigerant supply of the heat exchanger to open; S3. If the heat exchange device is used in a cold storage, execute the cold storage-specific control logic: (a) when the temperature of the first heat exchanger (door zone) is higher than the second temperature threshold, start the refrigerant supply; (b) when it is detected that the wind speed directed from the second heat exchanger (central area) to the first heat exchanger exceeds 3 m / s and the temperature of the central area is lower than the first temperature threshold, forcibly maintaining the refrigerant supply to the second heat exchanger; (c) Real-time monitoring of refrigerant pressure. If the pressure falls below a dynamic threshold, the refrigerant supply to the second heat exchanger is preferentially cut off; S4. If the heat exchange device is used in an outdoor power facility, execute the power facility-specific control logic: (a) When the temperature of the first heat exchanger (sun-direct-side) exceeds a second temperature threshold, the refrigerant supply to the first heat exchanger is started; (b) When the wind speed exceeds 4m / s and the temperature of the second heat exchanger (on the shady side) rises by more than 5°C within 10 minutes, the refrigerant supply to the second heat exchanger is forcibly started; (c) If the refrigerant pressure is insufficient, the second heat exchanger will be started and stopped intermittently according to the preset cycle (≤30 seconds); S5. When any of the following conditions is met, the refrigerant supply to the corresponding heat exchanger is shut off: (a) The temperature drops below the first temperature threshold; (b) The wind speed is lower than the scenario threshold (cold storage: 2 m / s; power facilities: 2 m / s); (c) The cold storage door remains closed for more than 30 seconds; S6. When the pressure difference across the filter cartridge exceeds 200 Pa or the refrigerant pressure remains below 200 Pa for more than 5 seconds, a maintenance alarm signal is generated and sent to the user terminal.

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